Humidity control system



April 17, 1951 A. TRASK 2,549,547

HUMIDITY; CONTROL SYSTEM Filed July 6, 1945 4 Sheets-Sheet 1 fi'zz/elz for: p llezz Trasfi @zwm/zggy April 17, 1951 I A. TRASK 2,549,547

I HUMIDITY CONTROL SYSTEM Filed July 6, 1945 4 Sheets-Sheet 2 J 2' 41/2 rz 20 7"-' 4, 22 272' ji asl April 17, 1951 A. TRASK HUMIDITY CONTROL SYSTEM 4 Sheets-Sheet 4 Filed July 6, 1945 11 1 1 1 1 1 1 .I 1 1 1 1 1 1 1 1 11 1 1 1 1 1 r 1 1 1/ 1 1 1 1 1/ 1 H 1 1 8 1 H 1 1 1 1 9 1 1 1 1 1 A 1 I// I 1 1 1 Q o 1 1 1 1 D 1 1 1 1 1 U U 1 11 11 1 1 I II 1 1 1 1 1 01 IV 11 1 I! I 1 1 1 6 ,1 2 1 3 11 1 1 9 Z /1 H 1 1 1 1 1d 11 0 1 1 7 1 7 1 1 7 ,1 1 1 1 1 1 1 1 1 1 1 1 1 1 11 7 1 1 1 1 1 1 1/1 1 1 I. 1 M 11 1 1 11 1 1 1 1 1 1 1 11 1 1 .1 1 11 11 11 1 11 11 1 11 1 1 1 1 11 11 1 1 11 1 1 11 1 1 1 1 1 Patented Apr. 17, 1951 UNITED STATES PATENT? oFFicE' HUMIDITYLCONTROLaSYSTEll/E Allen Trask, Chicago, Illil Application' July65.1945, Seria1 Nor6D3i-49lll This :invention relates: to mechanialrefrigeraatiorrsystem .f'or effectingzand maintainingiselectedi temperatures and selected relative humidities of air; within an enclosure.

In food refrigerators, comfort-air conditioned enclosures, storage: vaults; and in. certainuindusze trial processes itis highly desirabl'e tohave the'v mostadvantageous temperatures" and relative: humidities efiected and maintained automatie cally.

In" the refrigeration systems'now in general use for: accomplishing the dual purposeof controlling the I temperature and humidityof-' air within an enclosure; the relative humidityis neither-subject to 'selection bymeans of a: variable control, nor" is it automatically lield substantially: constant in spite of the influenceofvariable factors which normallycause-itto -fluctuate.' In the conventional systems humidity control is selectiveonly at the time of the originaldesignof the 20 system: An evaporatoris matchedto a condensing unit with the-relationship of heat ab'sorbing' capacity to'condensing capacity selected to'- pro-'-- duce approximately the required relative humi'd it'y under" average operating conditions: After 25 thisinitial selection' has been made; no provisions: are made for subsequent manual selective change in this' relationship.

The resulting humidity inthese" conventional I systems is 'determin'ed in" a general way by the temperature difference between the cooling sur-'=- face of the evaporator andj the air" it is cooling inan' enclosure: If 'a large coolingsurfaceis used in relation to the-condensing"unit capacity, the r thetemperature difference between'th'e air and the surface will be small; thus providing a high" dewpoint resulting in: a-higlrrelative-humidityi Conversely; if 1 the cooling surface'is'small in rela tion to the condensing unit capacity; then thetemperature difierence' will be proportionately great "to 1 provide a relatively 10W dewpoint and I? proportionately low-relative humidty:

In enclosuresrefrigerated by conventional" systems having a fiiced relation between the con densingtunit capa'city and theevaporat'or capac-' ity; it: is; not possible 170T.HIQZiIltEiHTWTSUEStaHtiaIIy fixedrelative ,humidityaunder the=variasbleiopers=- ating conditions; existing in the-majority ofinstalelations. The five; principal J. variables that; causes corresponding variations in relative humiditygarezi 50 thezfollowingz.

L Variations .;in.:ambient temperature; 2. Variations. of.enclos'edxairptemperaturegi 3. =Variationsin temperature'difierence betweem: enclosed ainand the evaporatorsurface 55 5:Cl'aim's.: (Cl. 62-6) 2:. 4; Variationsiof:condensing;unitrunningitimeig f and;

5 Variations: in. the amount: ofwater-vapor: entering or leaving the enclosure.

A: substantially. constant relative humiditygmay be maintained in: an:enclosures-equipped withx-al:

refrigeration system, whiohiis=subiected to one:

or moreis of. the above:fivervariablemonditions; if thersystem is I constructed: to automatically. comipensate each respective variable v by: an':.app ropri:--

ate functional response; One or- IIIOI'BSOflllhfiIfiVBZ for the. attainmenteaznd'rmaintenarrceziof; a:

stantially constant relative humidity withimam enclosure; 7

Another: object is'ito; provide: the:' automatic:

attainment. andsmaintenanoezof a substantiall e constant relativeJhumidityin ani enclosure by refrigeration system. adapted -.tozalternately 'PIO." duce two evaporator temperatures in response: to

relative humidity for whichthehumidostat is'set,

and; the. other. temperature. being lower than the dewpoint of'said relative Humidity for which. the;

humidostat is set.

A further objecti's to "provide automatic-control' of humiditywitlii'n acool'ed enclosure 'a'lter natively removing water" vapor andad'din'g water vapor totheair *of"saidenclosure in' response" to. the demandsofamanually*set-liumidostatf Still another object is to provide"a-' unitaryrefrigeration system wherein'motorheat and'heat of compression are used' toassist in the-automatic attainment-and inaintenance of manuall'yseleeted relative humidities.

Another: important obj ecti is' to provide for'ttlie removal of latentl he'at from water vapoi in an enclosureand: f or: utilizingzaiportioni off this-heat I forassisting in thezifurthergreduction ofitheirel-a tivenhumiditylof the: aim within the renclosureathe. demands .ofa selectively set. humidostat ones: temperature being above the dewpointv of; the

wall being shown;

A further object is to provide for the coincidental attainment and maintenance of both a substantially constant relative humidity and a substantially constant temperature in the air within an enclosure.

Still another object is to provide for the automatic control of both humidity and temperature by a refrigeration system whereby a selected relative humidity is attained and maintained as the primary objective, and as a secondary objective a selected temperature is attained and maintained only after the accomplishment of said primary objective.

With reference to the appended drawings in conjunction with the following detailed specifications and explanations, further objectives, purposes, and advantages of this invention will be understood.

In the drawings:

Figure l is a horizontal sectional view, partly in elevation, showing the internal refrigeration mechanism of a unitary air cooled system adapted for mounting in a side wall opening of a refrigerator;

Figure 2 is a vertical sectional view taken through the device shown in Figure 1, portions being shown in elevation;

Figure 3 is a more or less diagrammatic view showing the unit of Figure l and Figure 2 mounted in a refrigerator wall in its normal operative position, only a fragment of the refrigerator Figure 4 is a horizontal sectional View of a second embodiment of this invention showing the internal refrigeration mechanism of a unitary water cooled system adapted to be mounted on' the ceiling of a refrigerator;

Figure 5 is an enlarged vertical sectional view of the water evaporating pan that in Figure 4 is shown assembled on top of the motor-compressor unit, the view showing fragments of the water inlet and drain pipes;

Figure 6 is a transverse sectional View taken on the line 8-5 of Figure 4;

Figure 7 is a wiring diagram of the temperature and humidity control circuits used in the refrigeration system shown in Figure 4 and Figure 6;

Figure 8 is a top fragmentary sectional view of a third embodiment of this invention showing the internal refrigeration mechanism of a water cooled system adapted for merchandise vaults and comfort air conditioning;

Figure 9 is an enlarged side elevational view of the motor and linkage used to operate the air valve shown in Figure 8;

Figure 10 is a longitudinal sectional view, partially in elevation, of the device shown in Figure 8;

Figure 11 is an enlarged perspective view of the adjustable link connecting the motor lever to the air valve lever shown in Figure 9;

Figure 12 is a front elevational view showing the evaporator end of the system of Figure 8 and Figure 10;

Figure 13 is a diagrammatic view showing an electrical instrument control panel for regulating the functions of the refrigeration system shown in Figures 8 and 10;

Figure 14 is an electrical wiring diagram of the control panel of Figure 12; and

Figure 15 is a diagram of an enclosure wherein a unitary refrigeration system of the types shown in Figure 4 and Figure 8 is mounted on i the ceiling and connected with a control panel mounted on a wall.

For purposes of illustration, specific embodiments of the present invention have been selected. It is recognized, however, that many modifications will occur to the man skilled in the art without departing from the scope and spirit of the invention.

The first embodiment of this invention is a unitary, air cooled, refrigeration system adapted for controlling the temperature and relative humidity of a food refrigerator. It is shown in the drawings in Figures 1, 2, and 3, wherein cabinet I is divided into two compartments Ia and lb by an insulated partition 2, which is adapted to fit and be secured in a corresponding opening in the side wall of a refrigerator in which the unit is to be assembled and operated. The left-hand compartment Ia encloses an air cooled condensing unit comprising a motor-compressor unit 3, a fin tube condenser 4, and a receiver 5. The right-hand compartment Ib houses an evaporator I I.

A partition 6 in the left-hand portion of the cabinet has a centrally located opening registering with the air inlet opening of a centrifugal squirrel cage type blower I. The walls of cabinet I have openings radially opposite blower I, to provide an air discharge opening for said blower.

Blower I is mounted on shaft 8 which is journaled in bearings 9, mounted in insulated partition 2. Shaft 8 is connected to be driven by the motor of motor-compressor unit 3, by means of flexible coupling II]. In operation of the condensing unit air is drawn by blower I, through condenser 4 to extract heat, thence over motorcompressor unit 3 to cool it, through partition 6 and finally out of the cabinet radially of blower I in the direction of the arrows.

In the right-hand portion of cabinet I is a fin tube evaporator II, operably connected in the usual manner to the condensing unit in the lefthand end of the cabinet I. Fan I2 is mounted at the right end of shaft 8 and is adapted to blow air through evaporator I I in the direction indicated by the air flow arrows. An opening I3 in the top portion of cabinet I is arranged to be controlled in size by a manually movable slide I4. Said slide is adjjusted to provide the minimum opening required to admit a corresponding minimum quantity of air required for flow through evaporator I I which will allow evaporator II to reach the lowest dewpoint temperature required in the operation of the system. A partition I5 in cabinet I, acts as a shroud for fan I2 to direct air through evaporator II. A thermostatic expansion valve 29 (Figure 2) is used in the system.

In the lower part of the right-hand portion lb of cabinet I, is an opening I6 (Figure 2) arranged to be opened andclosed by hinged air valve Il. Said air valve I1 is connected by means of link I8, to solenoid I9, which opens and closes it in response to the demands of humidostat 2!]. Cabinet opening I6 admits anadditional flow of air to evaporator I I to increase its operating temperature and thereby raises the dewpoint at which water vapor will be condensed by the evaporator.

The compressor discharge conduit 2| has a solenoid valve'22 admitting refrigerant vapor directly from the compressor to the condenser 4 when it is open. When solenoid valve 22 is closed the compressor discharge vapor is forced to go V aerated;

- through an alternate, parallel, side. conduit 23 merge theremote portion discharge conduit 23 in pan 2.4.

Humidostat 2B: is of the double contact, two. circuit typeadapted'fon selective manual setting. A- contact to afirst circuit is madeuponthe demand for a reducedhumidity-.- Upon the closing of: this circuit solenoid I9 isenergized to close air-valve H. The-air flow-throug-h-evaporator ll is thereupon reduced to result inalower evaporator temperature below the dewpoint of the air being. drawn through theevaporator ll. watervapor is eliminated" from the air of a refrigerator in which the system is operating, and the relative humidity of the airis reduced. When the relative humidity of the air reaches the amount called for by the humidostat, said first contact is opened and air valve ll falls open by gravity.

When the relative humidity of the air surrounding humidostat 2iiis lower than that required by the humidostatsetting, a second contact closes a second circuit which energizes solenoid Valve 22. Thereupon hot compressor discharge refrigerant vapor is caused to flow through conduit 23 into condensate pan 2 4 Where it is submerged in water. The hot refrigerant vapor includes sensible and latent heat taken from the refrigerator in which the system is functioning, together with heat-of compression from the compressor, and electric motor heat taken from the electric motor parts disposed in heat exchange relationship with a portion of the compressor enclosing relatively cool refrigerant vapor as it is drawn from the evaporator ready to be compressed. Heat from all of these sources is transferred to the water in pan 24 and raises the tem perature and vapor pressure otth water. This heat causes the water in pan 24 to evaporate so as to increase the relative humidity in the refrig erator. When the relative humidity becomes increased to meet the requirements of humidostat 2D, the second contact opens and solenoid valve 22;-'opens in response thereto to stop the flow of hot discharge vapor to the water evaporating pan 24 through conduit 23;.

In this embodiment oftheinvention the motor- I compressor unit operation is controlled by the temperature demands; of thermostat 28. Required humidity correction takes place only during compress'ion cycles demanded by the thermostat; An air-cooled refrigeration system constructed in accordance with this embodiment of the invention has a wide humidity correction capacity to counteract the principal variables which operate to alter the required humidity duringthe offcycles of the refrigeration system.

A second embodiment of this invention i a unitary, water cooled, refrigeration system adapted for controlling the temperature and relativehumidity of a food refrigerator. It'is shown in Figures 4, 6, and '7, wherein a single cabinet is composed of two compartments; namely, a

closed; insulated compartment 35, and an open ended; uninsulated compartment Compartment -3.5senclosesawater cooled condensing unit' Thus comprising a. motor.-.compressorunit 31', and water cooled condenser-receiver unit 38, and a.

water; cooled fin coil 39 for extracting excessheat from the air in said compartment.

Referring to Figs. 4 to 6, compressor discharge tube Hll leads compressed refrigerant from the compressor 3.1. tothewater cooled condenser 38.

Tube I 02 carries the condensed liquid refrigerantv from the condenser 38. to expansion valve 5|.

Tube I03 connects expansion valve 5| to the inlet. Tube I04 from evaporator 45 carries refrigerant vapor to the suction inlet:

of the evaporator 45.

of" the compressor 31.

During operation of the condensing unit water control valve 48- admits cooling water to the con-.v denser-receiver 38, from which it flows throughpipe 4m to fin coil 3'9 and from which it is led out to a drain through pipe 42. A fan 43mounted on the motor shaft causes a circulation of the air within compartment 35. A partition 44 with an opening suitably registering with fan 43; i arrarnged to direct the flow of said internal air over motor-compressor unit to extract its surplus heat, then to direct said air over fin coil 39 which absorbs said surplus motor-compressor heat, and thence around to the suction side of fan 43 to complete a circuit.

In compartment 38 is an evaporator fin coil 45.

A fan 46, driven by a variable speed fan motor- 41 of the capacitor run type, blows air through evaporator 45 from which it is dispersed by defiector blades @8. Below fin coil 45 is a condensate pan shown at 49 in Figure 4 for collecting condensed water vapor. condensate to an outside drain system. A thermostatic expansion valve 5| meters refrigerant to the evaporator 45.

On the top of motor-compressor unit 31 is a pan 52 in heat exchange relation with said unit. A pipe 53 branches from pipe 4m to lead to pan 52 through a solenoid valve 54, which controls the flow of heated cooling water to pan 52. An overflow pipe 55 leads from pan 52 to drain pipe Eli (Figs. 4, 5 and 6). p

The wiring diagram Figure 7, indicates the instruments and electrical elementsof the refrigeration system which cause it to effect and maintain selected temperatures and relative humidity.

r -single pole relay 56, a humidostat 51, a variable transformer 58, and a thermostat 59 are mounted on a control panel 6|, and connected by suitable wiring as indicated to the fan motor 4?, the sole: noid' valve 54, and the compressor motor 31. A pair of mounting brackets 62 (Figure 6) is provided for mounting the entire unit on the ceiling.

Wire I i fiiFig. 7) is the neutral side of the current supply line to variable transformer 58, fan motor 27, solenoid 54, compressor motor 3'! and relay coil 5'5. Wire IH carries the opposite side of the current supply line to the variable transgrmer 58, relay 56, humidostat 5i and thermostat A rise in humidity above the setting of humidostatr'ii, causes humidostat 5? to make the upward contact, shown to energize relay coil 56- through wire l l2. tablish a circuit through variable transformer 58 to fan motor 4? to run it at a reduced speed in ac-,

cordance with the setting. ofthe transformer.

ate fan motor 4? at itsfullspeed.

A.. ducti umidi below e. t ne f 'f humidostat 57, causes humidostat 51 to make a.

A drain pipe 50 leads Relay. 56. then closes to es-' 7 downward contact shown, to complete a circuit to energize solenoid valve 54 through wire II5. Thermostat 59 controls the operation of compressor motor 31 by controlling the circuit from line wire III to the compressor motor through wire In operation the thermostat controls the operating time of the system by causing the condensing unit to function during the time the thermostat demands temperature reduction. The humidostat is of the double contact type having a first contact which completes a circuit upon the demand for a reduction of relative humidity, and a second contact which completes a circuit upon the demand for an increase of relative humidity. When the humidostat is satisfied by the existence of the selected relative humidity, no contact is made.

During the time that the required relative humidity exists and no change is called for by the humidostat, the fan motor 41 runs at its full normal speed. When a reduction of relative humidity is demanded said first contact is made to establish a circuit to fan 4?, through variable transformer 58, to reduce the speed of fan 46 to a predetermined minimum which reduces the volume of air flowing through the evaporator 45 and thereby produces in the evaporator 45 the temperature of the minimum dewpoint required in the functioning of the refrigeration system. Water vapor is then condensed and eliminated from the air of a refrigerator in which the system is functioning. When the required relative humidity is reached, said first humidostat contact is broken, fan motor 4! then attains its normal speed, the temperature of the evaporator 49 is raised above the dewpoint of the air being cooled, and condensation is stopped.

When an increase of relative humidity is required, a second contact is made in hum-idostat 51, completing a circuit to solenoid valve 54 to open it and supply water to pan 52. Here heated water from the cooling system is evaporated by the heat of the motor-compressor unit which includes sensible and latent heat taken from the refrigerator in which the system is functioning, also heat of compression from the compressor, and electric motor heat taken from the electric motor parts in heat exchange relationship with the compressor body and pan 52. The Water vapor so produced within insulated compartment 35 escapes therefrom through opening 53 to increase the relative humidity of the refrigerator in which the system is operating. The occurrence of the required increase of relative humidity caused said second humidostat contact to be broken and thereupon solenoid valve 54 closes to prevent additional water from being evaporated in pan 52.

Referring to Figure 5, it will be seen that the height of the projection of drain pipe 55 into evaporating pan 52 will determine the amount of water remaining to be evaporated at the time the satisfied humidostat closes the solenoid valve 54. By this means water vapor is discharged beyond that required to open the humidity increase contact of the humidostat 5'1, but not in an amount suficient to close the humidity reduction contact of the humidostat.

A water cooled refrigeration system constructed in accordance with this embodiment of the invention, has a wide humidity correction capacity to counteract the principal variables which operate to alter the required humidity during the off cycles of the refrigeration system,

A third embodiment of this invention is a unitary, water cooled, refrigeration system adapted for controlling the temperature and relative humidity of enclosures requiring moderate temperature reduction, and relative humidity in the range of 50% to 70%, for comfort air conditioning or the conditioning of the air in such enclosures as vaults for the storage of furs, Woolen garments, or other merchandise.

This embodiment is shown in Figures 8 to 12, inclusive, wherein a single cabinet I0 encloses a water cooled condensing unit comprising a motor-compressor unit II, and a condenserreceiver unit I2. At the right-hand end of cabinet ID, is a fin tube evaporator coil I3, to which refrigerant is metered by thermostatic expansion valve I4. A fan I5 is mounted on the end of the compressor motor shaft to draw air through evaporator "I3, and discharge it over motor-compressor unit I I for cooling it. A partition I6 in cabinet 10 has a circular opening arranged in relation to fan I5 as a shroud to direct the flow of fan moved air as above described. A pair of mounting brackets 17 is provided for mounting the entire unit on the ceiling of a room.

In the top of cabinet I0 is an opening I8 (Figure 10) arranged to be closed by a hinged air valve I9. An arm (Figure 8) and lever 8| are connected to air valve 19 for opening and closing the valve. A two position electric damper motor 82 is operatively connected to air valve lever 8| by means of adjustable link 83, for opening and closing air valve I9.

Adjustable link 83 shown in Figure 11, comprises a first bar 84 provided with two fixed collars 85. A second bar 86 is arranged to slide in collars 85, longitudinally of bar 84, to a minimum combined length adjustably fixed by stop screw 81. The latter being fixed with respect to bar 86. A coil spring 88 tends to hold bar 84 and bar 86 at the minimum combined length determined by the position of screw 81.

Evaporator I3 is provided with a condensate drain pan 89 having a drain pipe 90. A cooling water inlet pipe 9I feeds the water cooled condenser I2 through a water control valve 92. Cooling water is discharged from the condenser to the drain through pipe 93.

Compressor discharge tube I05 and 10) leads compressed refrigerant vapor to water cooled condenser I2. Tube I95 conducts discharge vapor pressure to water control valve 92. Tube IB'I leads condensed liquid refrigerant from the condenser 12 to expansion valve I4. Tube I98 leads refrigerant at a reduced pressure from expansion valve I4 to the inlet of the evaporator I3. Tube I09 leads refrigerant vapor from evaporator I3 to the suction inlet of compressor II to complete the refrigerant circuit.

In operation this refrigeration system is controlled by an electric circuit illustrated by the instrument panel shown in Figures 13 and 14, wherein a push button switch 94, a single circuit humidostat 95, a relay 96, and a thermostat 91 are mounted on a panel board 98. A hygrometer 99 and a thermometer I are provided as direct indicating instruments. In Figure 14 a Wiring diagram of these instruments is shown and is adapted to cause the system to attain a selected relative humidity as its primary objective, and a selected temperature as its secondary objective. 7

Wire I20 (Fig. 14) is the neutral side of the current supply line to relay 96, damper motor 82 and compressor II. Wire I2I carries the opposite (see Figs. 8

side of the current supplyl-ine to manual switch I 94, and thence through wire I 22 to humidostat 95. Arise-in humidity above the setting of humido- I "stat95, closes the humidostat contact to estabestablishes a-circuit-to damper motor 82, causing it to move to its open position. Wire I25 establishes a circuit to compressor II.

When humidostat 95 is satisfied its contact opens to break the circuit through wire I23 to relay 96. Then relay 96 closes its lower set of contacts to establish circuits through wire I26 andwire I21. Wire I26 establishes a circuit to damper motor 82, causing it to move to its closed position. Wire I21 establishes a circuit to thermostat 91 which in turn then controls compressor II through wire I25.

When the relative humidity of an enclosure, such as is diagrammatically represented in Figure 15, is in excess of the required amount for which the humidostat 95 is set, then damper motor 82 actuates link 83 to cause air valve I9 to open to the position as shown in Figures 8 and 10. Fan I then draws a portion of its air through evaporator I3 and a portion'through opening IS. The air flow reduction through the evaporator reduces its heat load, and the condensing unit causes the evaporator temperature to drop below thedewp-oint of the ambient air. By means of adjustable air valve link 83, the size of the air inlet opening may be initially controlled. The air valve opening is adjusted to give the maximum permissible evaporator temperatures over the frosting point.

When the desired humidity is reached humidostat 95 causes damper motor 82 to close air valve I9, and include thermostat 9! in the compressor motor circuit. The full air capacity of fan I5 is then drawn through evaporator I3 to raise its temperature above the dewpoint of the ambient air. Sensible heat only is then extracted from the air until thermostat 91 is satisfied.

In this embodiment of the invention, heat of the motor-compressor unit II is used to assist in the reduction of relative humidity by causing it to reheat air drawn through the evaporator. In the proportion that the motor-compressor unit is cooled by the air fan I5 blows over it, that air is heated and its relative humidity thereby reduced. The heat so used for assisting humidity reduction includes electric motor heat, heat of compression, and both latent heat and sensible heat of the air conditioned by the refrigeration system.

This specification makes it apparent that each of the three embodiments of this invention comprises a novel structure and control means for removing varying proportions of water Vapor denser and a-condenser fanin said refrigeration from the air of an enclosure: while maintaining V its temperature between close predetermined fixed limits.

It will also be understood that each of the three embodiments of this invention include means using the heat developed in the functionparting from the spirit and scope of the invention as'di sclosed' and clai-med, and that I-do not desire to limit theinvention to the exact construction herein set forth.

I claim as my invention:

1. An enclosure for a refrigerated space, an

opening in said enclosure, a cabinet adapted to be inserted partially through said enclosure opening, a refrigeration system .in said cabinet, a partition in said cabinet adapted to plug said enclosure opening; a compressor, a motor, a consystem assembled within the portion of said cabinet not inserted within said enclosure; an evaporator, and an evaporator fan assembled within the portion of said cabinet adapted for insertion into said enclosure; a humidostat, means responsive to said humidostat for changing the C. F. M. flow of air through said evaporator from a maximum to a. minimum flow, and means for changing the C. F. M. of said minimumflow.

2. An enclosure for a refrigerated space, an opening in said enclosure, a cabinet adapted to be inserted partially through said enclosure opening, a refrigeration system in said cabinet, a partition in said cabinet adapted to plug said enclosure opening; a compressor, a motor, a condenser, and a condenser fan in said refrigeration system assembled within the portion of said cabinet not inserted within said enclosure; an evaporator, and an evaporator fan assembled within the portion of said cabinet adapted for insertion into saidenclosure; a humidostat, and

. variable means responsive to said humidostat for changing the C. F. M. flow of air admitted to the suction of said evaporator fan.

3. An enclosure for a refrigerated space, an opening in said enclosure, a cabinet adapted to be inserted partially through said enclosure opening, a refrigeration system in said cabinet, a par- T tition in said cabinet adapted to plug said enclosure opening; a compressor, a motor, a condenser, and a condenser fan in said refrigeration system assembled within the portion of said Cabinet not inserted within. said enclosure; an evaporator, and an evaporator fan assembled within the portion of said cabinet adapted for insertion into said enclosure; a humidostat, an air valve in said cabinet located to admit air to said evaptition in saidcabinet adapted to plug said enclosure opening; a compressor, a motor, a condenser, and a condenser fan in said refrigeration system assembled within the portion of said cabinet not inserted within said enclosure; an evaporator, and an evaporator fan assembled within the portion of said cabinet adapted for insertion into said enclosure; a humidostat, a manually adjustable opening for admitting a vminimum C. F. M. air flow to said evaporator fan, and an adjustable air valve for admitting an additional air flow to said evaporator fan in response to said humidostat. x

' 5. In a unitary refrigeration system of the compression'type, an evaporator, a fan for circulating air through the evaporator, a humidostat, means responsive to said humidostat for changing the C. F. M. flow of air through said evaporator from a maximum to aminimum flow,

and means for changing the C. F. M. of said minimum flow.

ALLEN TRASK.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date Williams Mar. 6, 1934 Number 

